Apparatus for controlling the variation of silver delivered from a carding machine

ABSTRACT

The invention comprises a method of and means for controlling the count of a sliver while being fed from a carding machine to ensure a substantially uniform sliver, the sectional size of the sliver being related to a valve setting and passed through sensing means so that any slight variation in the sliver size is sensed and magnified to operate the valve which operates a fluid motor which in turn operates variator control means capable of causing correction of the sliver size.

United States Patent Varga 1 Feb. 29, 1972 [541 APPARATUS FORCONTROLLING THE VARIATION OF SLIVER DELIVERED FROM A CARDING MACHINE[72] Inventor: John Maximilian Jules Varga, Toronto,

Ontario, Canada Carding Specialists (Canada) Limited, Toronto, Canada 22Filed: Aug. 29, 1969 [21 Appl.No.: 854,170

[73] Assignee:

[30] Foreign Application Priority Data Sept. 3, 1968 Great Britain..41,750/68 [52] US. Cl [51 Int. Cl. [58] Field of Search ..19/239, 240,241

[56] References Cited UNITED STATES PATENTS Selby 19/240 FOREIGN PATENTSOR APPLICATIONS 912,146 12/1962 Great Britain 19/241 930,873 7/1963Great Britain 19/240 612,891 11/1960 Italy ..19/240 PrimaryExaminer-Dorsey Newton Attorney-Stevens, Davis, Miller & Mosher [57]ABSTRACT The invention comprises a method of and means for controllingthe count of a sliver while being fed from a carding machine to ensure asubstantially uniform sliver, the sectional size of the sliver beingrelated to a valve setting and passed through sensing means so that anyslight variation in the sliver size is sensed and magnified to operatethe valve which operates a fluid motor which in turn operates variatorcontrol means capable of causing correction of the sliver size.

10 Claims, 11 Drawing Figures Patented Feb. 29, 1972 3,644,964

9 Shuts-Sheet 5 INVENTORZ 59 "FIG. 3A"

Patented Feb. 29, 1972 3,644,964

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9 Sheets-Shoot 8 Patented, Feb. 29, 1972 9 Sheets-Shoot 9 NQE O 92 hm?mm wmr & r/ /////////v///// APPARATUS FOR CONTROLLING THE VARIATION OFSILVER DELIVERED FROM A CARDING MACHINE This invention relates to theformation of slivers in carding machines.

It is often difficult to maintain a high degree of uniformity in sliversduring processing and various methods and means have been tried to solvethis problem. The main object during the formation of slivers is to tryand keep a constant count, i.e., weight per unit length, and it is theobject of this invention to provide an improved arrangement for thispurpose.

The optimum type of feed back for the automatic correction of sliverregularity when using so-called closed loop or integrating controlsystems is of a graduated type where the correction is at all timesdependent on the degree and sense of the error signalled. Closed loopautolevellers in the past have tended to have complex electronic controlsystems in order to provide smooth correction, or have compromised withon-off controls with a band around the neutral position where nocorrection is generated.

According to this invention a method of controlling the count of sliversfed from a carding machine consists in relating the sectional size of asliver to a normal setting of valve control means, sensing said givensliver sectional size in relation to said setting during linear movementof the sliver, causing any variation in such sliver size from nonnal tomove the valve from its set position and thus control the direction andrate of flow of fluid to a fluid motor to cause said motor to controlvariator control means capable of causing correction of the sliver size,and arranging any particular position of the variator control means tocorrespond with a given speed ratio but not correspond to a givenposition of the sensing means.

The invention includes apparatus comprising sensing means having sliverengaging surfaces, at least one of said surfaces being movable relativeto the other to sense variation in sliver thickness from a giventhickness related to a normal setting of valve control means, levermeans operable by movement of said one of said surfaces to provide amagnified movement, said valve control means being responsive to saidmagnified movement to control the direction and rate of flow of fluid toa fluid motor, said motor being adapted to operate variator controlmeans capable of causing correction of the sliver size, any particularposition of the variator control means being arranged to correspond witha given speed ratio but not to correspond to a given position of thesensing means.

The fluid pressure control system according to this invention ensures afully continuous control in a very simple manner. Moreover, the shape ofthe control curve can be tailored to any form by known modification ofthe lands of the control valve.

In order to make easier the construction and shaping of such a valve, itis important to give it the maximum degree of movement for a givenmovement of the sensing means which is very small in general. Bycoupling the valve to the end of a reasonably linearly magnifyingleverage system, it is possible to construct a very simple, reliable andrugged valve, not sensitive to dirt and contamination and enabling it tobe put on to ball bearings.

A particular embodiment of the invention will now be described in moredetail, by way of example, with reference to the accompanying drawingsin which:

FIG. 1 is a schematic view of the general assembly of the completeapparatus;

FIGS. 2A and 2B show a part side elevation part section of part of thecontrol apparatus;

FIG. 3 is a section on line llI-lII of FIGS 2A and 23;

FIG. 3A is a section on line 3A of FIG. 3;

FIGS. 4A and 4B show a section on line IV--IV of FIGS. 2A and 28;

FIGS. 5A and 5B show a cross section on line V-V of FIGS. 2A and 28;

FIG. 6 is an end elevation partly in section of a further part of theassembly; and

FIG. 7 is a side elevation of the part shown in FIG. 6.

Referring now to FIG. 1 this shows a carding machine 1 fed with a web ofcotton 2 by a lap feed 3. Carded cotton leaving the machine enters acondensing trumpet 4 and from there passes between two rollers, an upperroller 5 and a lower roller 6. The upper and lower rollers are drivenfrom the drive to the carding machine. The upper roller 5 is rotatablycarried by one member of a lever system indicated generally at 7, sothat the upper roller can move relative to the lower roller. Thesemovements take place in response to variations in thickness of a sliverpassing between the rollers and this movement is magnified by the leversystem 7 to give a magnified movement at an end 8 of a lever formingpart of the system. The end 8 is connected to a spool 9 of a spool valve10 and the spool controls flow of low pressure fluid from a pump 11driven from the carding machine drive. The spool 9 has two landscontrolling outlet ports 12 and 13 from the housing 10, and the outletports 12 and 13 are connected to pass fluid to opposite sides of apiston 14 working in a cylinder 15. The piston 14 has a piston rod 16which is connected to means for shifting a belt 17 of a cone belt drive.The drive comprises a driving roller 18 coupled to the drive to thecarding machine and a driven roller 19 coupled to control the speed ofthe lap feed roll 3.

In operation of the system when the sliver passing between the rollers 5and 6 is of a desired thickness the spool 9 is in a neutral positionwherein the lands close the outlet ports 12 and 13 so that the piston 14takes up its neutral position and the belt 17 is positioned on the conesso that the lap feed roll is driven at a desired speed. If the variationin sliver thickness occurs then the upper roller 5 is moved from itsnormal position and so moves the lever system. The magnified movement atthe end 8 of the lever system shifts the spool 9 to uncover the outletport 12 or 13 and allow pressure fluid to pass to one side of the piston14. The piston thus moves so shifting the belt 17 to vary thetransmission ratio between the cones 18 and 19 and thus to change thespeed of the lap feed roll 3. The change of speed is efieeted in a sensesuch that it will tend to cause the sliver to return to the desiredthickness, and once the sliver has resumed this thickness the systemreverts to its neutral condition. The remaining figures show theapparatus in more detail.

Referring to FIGS. 2A and 4A the rollers 5 and 6 between which theslivers pass are of conventional male and female configuration, theroller 6 being formed with a groove 20 in which a rib 21 of the roller 5fits. The roller 6 is made up of two parts 22 and 23 bolted together bybolts 24 on either side of a spacing member 25 having a width equal tothe desired width of the groove 20. From the rollers 5 and 6 the sliverpasses to a standard knockoff motion indicated generally at 26. This isof well-known construction and need not be described in detail save tomention that it acts to stop the carding machine if the sliver breaks.

A drive shaft 27 is coupled to the drive for the carding machine and isjournaled in bearings 28 and 29 secured to a lower housing 30. A gear 31is splined at 32 to the shaft 27 and meshes with a further gear 33splined at 34 to a shaft 35 running in bearings 36 and 37 mounted in anupper housing 38. The gear 33 meshes with a gear 39 splined at 40 on oneend of a further shaft 41 extending parallel to shaft 35. The shaft 41is mounted to rotate in bearings 42 and 43 supported in one arm 44 of abellcrank lever 45. The other end of shaft 41 has the roller 5 splinedthereto at 46. The end of shaft 35 remote from the gear 33 is splined at47 to the lower roller 6. The gearing is such that the rollers 5 and 6are both driven at the same speed.

A flexible diaphragm 48a is secured by a clip 49a to the arm 44 of thebellcrank lever 45, and is secured by a cover plate 50a to the upperhousing 38. The diaphragm 48a allows relative movement of the bellcrank45 in the upper housing 38 yet prevents dust and moisture from enteringthe upper housing 38.

Referring now to FIGS. 2A and 5A the bellcrank lever 45 is secured tothe outer races 46 and 47 of two bearings 48 and 49 the inner races 50and 51 of which are secured to a shaft 52.

The shaft 52 has a stub 53 which is eccentric to the axis of the shaft,and the stub 53 is rotatably mounted in the upper housing 38. At the endof the shaft 52 remote from the stub 53 there is secured by bolts 54 aknurled adjustment member 55 which is coaxial with the stub 53 and thuslies eccentric to the shaft 52. The knurled member 55 is located againsta distance piece 56 secured to the upper housing 38 by bolts 57 andforming a locating member for locating shoulders 58 on the shaft 52. Itwill be seen that rotation of the knurled member 55 causes the pivotalaxis of the bellcrank 45, Le, the axis of the shaft 52 to be movedrelative to the housing, and thus allows the distance between the axesof the rollers and 6 with the bellcrank lever in a given angularposition to be adjusted.

As shown best in FIG. 3 the bellcrank lever 45 has a lower arm 59terminating in bifurcated sections 60 and 61. The bifurcated arm 60surrounds a shaft 62 which is rotatably mounted relative to the arm 60by a combined bearing and sprag clutch 63. As shown in FIG. 3A, combinedbearing and sprag clutch 63 comprises bearings 63A positioned betweensurface 638 of shaft 62 and outer race 63C. The shaft 62 is supportedfor rotation relative to the arm 61 by a conventional ball bearing 64,and the shaft 62 carries at one end a gear 65. The shaft is locatedrelative to the various parts by grooves and circlips 66.

Located between the bifurcated arms 60 and 61 of the lower arm 59 of thebellcrank lever is the upper end of a magnifying lever 67. The lever 67also surrounds the shaft 62 and relative rotation between the lever andthe shaft is again allowed by a combined bearing and sprag clutch 68.The lever 67 is pivotally mounted by a bearing 69 about a shaft 70having a larger diameter section 71 and a smaller diameter section 72between which is formed a shoulder 73 against which the bearing 69 islocated. The larger diameter section 71 carries a stub 72 which isjoumaled by way of a bearing 73:: in one arm 74 of a bifurcated controllever 7613. The smaller diameter end 72 of the shaft 70 is secured tothe inner race of a bearing 75, the outer race of which is fixed to theother arm 74a of the control lever 76c. A distance piece 77 separatesthe bearing 75 from the bearing 69. The end of shaft 70 remote from theend 72 has secured thereto a gear 78 which meshes with gear 65 carriedby the shaft 62.

The pivoting of the bellcrank lever 45 in the housing by the bearings 48and 49, the pivotal connection between bellcrank lever 45 and magnifyinglever 67 by way of the combined bearing and sprag clutches 63 and 68,bearings 64 and shaft 62, and the pivoting of magnifying lever 67 to thelever 76c by bearing 69 round shaft 70 together with the freedom oflever 76c to pivot around the axis of bearings 80, 81, combine toprovide a lever system which is virtually friction free. All contactsbetween the various relatively movable members are rolling contactsrather than sliding contacts. Bearings which are subjected to very smallmovements at reasonable loads may have a tendency for the balls to sliderather than roll and thus to break down the lubricating film between theballs and the races, an effect known as false brinelling. This effect issubstantially reduced in the lever system disclosed by the presence ofthe combined bearing and sprag clutches 63 and 68. These act so that anysmall movement of the levers acts to rotate the shaft 62 in one senseonly and this positive rotation of shaft 62 ensures rolling contactbetween the balls and the races and thus prevents or reduces falsebrinelling. The connection from shaft 62 by way of gears 65 and 78 toshaft 70 ensures that shaft 70 is rotated with shaft 62 and reduces orprevents false brinelling in bearing 69 and in the bearing 75 betweenshaft 70 and control lever 760.

The control lever 76c acts to control the position of shaft 70 relativeto the housing. The bifurcated arms of the lever 76c are secured to acage 79 in which are secured the outer races of two bearings 80 and 81,the bearings being retained by circlips 82 and 83. The inner races ofthe bearings surround a shaft 84 having eccentric ends 85 and 86supported by bearings 87 and 88 respectively in a cage 89. The cagecomprises an upper section 90 bolted by bolts 91 to the upper casing 38,and a lower section 92 bolted by bolts 93 to the upper section 90. Theeccentric end of shaft 84 is pinned to an arm 94 having an upper part towhich is secured by a pin 95 one end of a tension spring 96, the otherend of which is secured by a pin 97 to the upper housing 98. The lowerpart of arm 94 has a surface 95a bearing against an adjusting member96a. The adjusting member 96a extends through a bore in a guide sleeve97 a secured by bolts 98 to the lower housing 30. The bore has athreaded section 99 with which a threaded section 100 on adjusting rod960 engages, and the end of the adjusting rod 96a carries a knurledadjusting member 101. The eccentric end 86 of the shaft 84 is driven bya pin 102 secured to a member 103 rotatably mounted in a bore in asleeve 104 secured by bolts 105 to the lower housing 30. The end of themember 103 has secured thereto a handle 106.

It will be seen that rotation of the knurled member 101 will cause theadjusting rod 960 to move in the sleeve 97a to control the angularposition of the arm 94 and thus of the shaft 84. Rotation of the shaft84 about the bearings surrounding the eccentric ends 85 and 86 changesthe height of the shaft 84 and thus of the control arm 76. This motionis in turn transmitted back to the bellcrank lever and acts to give afine adjustment of the distance between the axes of the rollers 5 and 6.Rotation of the handle 106 through 180 from the position shown gives anoverriding quick release to the shaft 84 to move this substantially sothat the lever system is moved to such an extent that the rib 21 onroller 5 lifts out of the groove 20 on roller 6 to allow any blockage ofthe sliver in the groove to be cleared. Return of the quick releasehandle 106 to its original position restores the lever system at itsoriginal adjustment. The tension spring 96 acts on the lever 94 toensure it always returns to its rest position with a constant force thusensuring the maintenance, with great accuracy, the set angular positionof the eccentric shaft 84.

As best shown in FIG. 2B the magnifying lever 67 extends downwardly andterminates at its lower end in a member 107 to which a roller 108 isrotatably secured. The lower end of this lever 67 lies adjacent to avalve shown generally as 109 for controlling a flow of hydraulic fluid.The valve 109 comprises a housing 110 in which a spool 111 is axiallyslidable. The spool is supported within the housing by ball or rollerbearing systems 112 and 113. The bearing system maybe either arecirculating system or a planetary system. In the recirculating systema sleeve member is positioned radially between the spool and thehousing, and balls are positioned between the spool and the sleevemember and between the sleeve member and the housing so as to be guidedfor circulation axially along both surfaces of the sleeve member andaround the ends of the sleeve member to pass from one to the othersurface thereof. In a planetary system the balls are axially retained ina cage which is positioned radially between the spool and the housing,and are in contact with both the spool and the housing. The spool 111,bearing systems 112 and 113, and housing 1 10 are assembled as a unitand fitted within a bore 114 formed in a block 115 (which may or may notbe part of the lower housing 30a) drilled with conduits for hydraulicfluid. The valve assembly is secured in position within the bore 114 byan end plate 116 and bolts 117, such plate acting against the spring116a which pushes the housing 110 against the circlip 1161;. One end ofthe spool 111 has secured thereto at 118 one end of a tension spring 119anchored at the other end to a pin 120 secured to the lower housing 30.The spring 119 acts to bias the spool into engagement with the roller108 at the lower end of the magnifying lever 67. It will thus be seenthat movements of the magnifying lever 67 will result in correspondingmovements of the spool 1 11. Moreover the spring 119 also serves to biasthe bellcrank lever 45 so that the upper roller 5 is pressed intoengagement with a sliver so as to respond to every small variation inthickness of the sliver. Such spring action may be augmented or replacedby a tension spring 119a, although a compression spring may be used. Ifthe spring 119 is dispensed with then the roller 108 and the end 118 ofthe piston 111 may be held together by a magnetic force.

The housing 110 is formed with a fluid inlet port 121, two fluid outletports 122 and 123 and two fluid drain ports 124 and 125, all of whichcommunicate with appropriate ducts drilled in the block 115. The spool111 is formed with two lands 126 and 127, which, when the spool is inthe neutral position shown in FIG. 23 cover the outlet ports 122 and 123respectively. The lands 126 and 127 are placed and tapered in a mannerto regulate fluid flow and direction dependent on the degree and senseof the displacement. They are designed so that they do not contact thesurface of the housing 110 in any position of the spool. Thus, the onlycontact between the spool and the housing is by way of the ball systems112 and 113 and all contact is rolling contact rather than slidingcontact so rendering the valve essentially friction-free.

Preferably, the hydraulic system controlled by this valve operates atlow pressure and this low pressure means that fluid leakage past thelands 126 and 127 is small. What leakage there is either passes equallythrough outlet ports 122 and 123 or completely around the lands 126 and127 to pass to drain through drain ports 124 and 125.

Fluid is pumped to the inlet port 121 by a pump indicated generally at128 and shown in FIGS. 2A, 2B, 4A and 4B. The pump is a self-portingtwo-stroke pump having pistons 129 and 130 working in cylinders 131 and132 respectively, fluid flow to each cylinder being controlled by avalve element 133 or 134 carried on the piston 129 or 130 working in theother cylinder. The valve annuli 132a connect with their correctcylinders respectively by appropriate channels in covers 1311; and 13212which also have in them the main inlet and outlet ports. Each piston 129and 130 is secured by a pin 135 and 136 to a connecting element 137 and138 respectively. The elements embrace eccentrics 139 and 140respectively splined at 141 onto the drive shaft 27. Rotation of thedrive shaft 27 thus operates the pump to pump fluid drawn from areservoir (not shown) from the cylinders 131 and 132 through suitableconduits to the inlet port 121 of the valve 109. The strokes of the twopistons are spaced apart by 90 and although this gives an unequal flowof fluid this is not found to be important. It will be appreciated thatthe pump described can be replaced by any other pump which can be drivenoff drive shaft 27 and deliver hydraulic fluid at low pressure to theinlet port 121 of valve 109. The fluid from the pump is divided betweenthe valve 109 and between a conduit 128a opening into a cylinder 129a inwhich is located a plug 130a having a helical path cut round the outersurface thereof. Fluid from the cylinder 129a can pass along the helicalpath 130a to an outlet 131a which is connected to drain. A peg 132aextends into the cylinder and engages the helical groove on the plug130a and the plug is extended out of the cylinder 129a and is formedwith a knurled ring 133a by which the plug may be rotated. Rotation ofthe plug causes the plug to move axially along the cylinder by virtue ofthe engagement of the peg with the helical groove. A sealing ring 134ais provided to prevent leakage of hydraulic fluid from the cylinder pastthe plug.

The plug 130a constitutes an hydraulic resistance through which part ofthe fluid from the pump passes and it is found that by splitting theflow between this resistance and the valve the volume of fluid enteringthe valve is directly proportional to the speed of the pump and isindependent of temperature or viscosity variations in the fluid.Movement of the plug varies the hydraulic resistance offered by this andthus acts to vary the relative volumes of fluid passing through the plugand into the valve.

The outlet ports 122 and 123 from the valve 109 are connected bysuitable conduits to opposite sides of a piston 135a working in acylinder 136a. The cylinder 136a is formed in the block 115 and isclosed by a closure member 137a secured to the block by bolts 138a.Sealing rings 139a and 140a are provided between the closure member 137aand the cylinder 136a and between the closure member 137a and a pistonrod 141a respectively. Movement of the valve spool 111 axially from theneutral position shown in FIG. 2B connects the inlet port to theappropriate outlet port so that fluid passes into the cylinder 136a onone side of the piston 135a. Fluid from the other side of the piston135a is exhausted from the cylinder 136a through the other outlet portand the drain port 124 or at the appropriate end of the valve. Movementsof the valve spool 111 in response to movements of the magnifying lever67 thus direct fluid to the cylinder 136a to move the piston a. Thespeed and direction of movement of piston 135a is thus at all timesdirectly related to the position of roller 5. Thus any slight or othermovement of the sliver sensing roller 5 from its setting causes the mainspool valve 111 to control the rate of flow of pressurized fluid to aselected side of the piston 135a depending upon the distance the valve111 has moved from its neutral position. This valve movement will varythe output shaft speed.

Movement of the piston 135a is used to control the position of a belt ina variable cone belt drive shown in FIGS. 6 and 7. The end of the pistonrod 141a has secured thereto a supporting member 142 carrying a framework 143. The framework 143 lies between an upper driving cone 144 and alower driven cone 145, the two cones being tapered in oppositedirections. A belt 146 engages the two cones to transmit rotationtherebetween and the framework 143 lies between the two runs of thebelt. The upper end of the framework'carries two horizontal arms 147 and148 lying below and adjacent to the upper cone 144 and projectingtowards the run 149 of the belt 146. Each arm 147 and 148 rotatablycarries at its end a roll 150 and 151 respectively having a horizontalaxis transverse to the axis of cone 144, and the two rolls 150 and 151engage opposite side edges of the run 149 of the belt, i.e., the beltpasses between the two rolls.

The lower end of framework 143 also carries two horizontal arms, one ofwhich is shown at 152 lying above and adjacent to the lower cone 145 andprojecting towards the run 153 of belt 146. Again each arm rotatablycarries at its end a roll such as 154 having a horizontal axistransverse to the axis of cone 145 and the two rolls such as 154 engageopposite edges of the run 153 of the belt, i.e., the belt passes betweenthe two rolls.

Pivoted at 155 to the upper end of the framework 153 is one end of anarm 156 projecting downwardly and towards the run 153 of the belt andhaving a first tensioning roll 157 rotatably mounted about an axis 158.The tensioning roll 157 engages the outer face of the run 153 of thebelt.

Pivoted at 159 to the lower end of the framework 143 is one end of asecond arm 160 projecting upwardly and towards the run 149 of the belt,and having a second tensioning roll 161 rotatably mounted at its freeend about an axis 162. The tensioning roll 161 engages the outer face ofthe run 149 of the belt. Two tension springs 163 and 164 span the tworuns of the belt, and opposite ends of the springs are anchored to thearms 160 and 156 by way of pins 165 and 166 respectively. The springs163 and 164 bias the tensioning rolls 157 and 161 towards each other topush the two runs of the belt towards each other and so tension thebelt. As the springs 163 and 164 act simultaneously on both tensioningrolls 157 and 161 the tensioning forces are equalized on the two runs ofthe belt and any deflecting forces on the framework 143 are minimized.

It will readily be seen that movement of the piston rod will cause thebelt 146 to move axially along the cones 144 and 145 and thus willchange the transmission ratio between the two cones.

The cone 144 is mounted on the driving shaft 27 as follows. The shaft 27is split into two coaxial sections parts 27 extending into lower housing30a and a part 167 connected to the drive mechanism of the cardingmachine. The cone 144 is hollow and one end thereof is connected bysplines 168 to shaft portion 167, the other end being connected bysplines 169 to the shaft portion 27 Grub screw 170 and 171 are providedfor locking the cone axially in position on the two shaft sections. Thegrub screws 170 and 171 may be released to allow the cone to be movedaxially to the left along shaft section 167 as seen in FIG. 6 to allowthe right-hand end of the cone to move past and expose the gap 172between the ends of the shaft sections 167 and 27. The belt 146 can thenbe slipped off the right-hand end of the cone 144 and withdrawn throughthe gap 172 to allow replacement of the belt. The old belt may simply bewithdrawn from the left-hand end of the lower cone 145 which is free. Anew belt can then be fitted by fitting on to cone 14S and then beingpassed through gap 172 and placed over the end of cone 144. The cone 144is then returned axially to its original position covering the gap 172and the grub screws 170 and 171 are tightened to lock the cone in itsdesired axial position.

The lower cone 145 is secured to an output shaft 173 by splines (notshown) and locating grub screws 174 and 175. The shaft 173 is supportedto run in bearings 176 and 177 carried by the lower housing 30, alabyrinth seal being provided in association with bearing 176 and acover plate 179 being secured by bolt 180 to the lower housing 30a atthe end 177 of the shaft. The seal 178 and cover plate 179 prevent theescape of oil from the lower housing 30a. The shaft 173 is formed with aworm section 181 with which a pinion 182 meshes. The pinion 182 iscarried by a shaft 183 suitably joumaled in the housing 30, and theshaft 183 is connected by means (not shown) to the lap feed of thecarding machine.

Thus, whenever the belt 146 is axially shifted to vary the transmissionratio between the cones 144 and 145 the speed of the shaft 173 isadjusted and this speed is transmitted by worm and pinion 181 and 182 tothe shaft 183 to drive the lap feed roller at a variable speed.

Operation of the complete system will now be apparent. The position ofthe lever system is set by coarse adjustment member 55 and fineadjustment member 101 so that when a sliver of the desired thicknesslies between the rollers and 6 the belt comes to rest approximately atthe center of the cones while the spool 111 is hovering about itsneutral position shown in FIG. 2B. Drive transmission between the conesis thus at a l/ 1 ratio so that shaft 173 is driven at the same inputspeed as shaft 27. The shaft 183 is thus driven at a speed proportionalto that of input shaft 27, and this acts to control the lap feed,feeding cotton into the carding machine. After carding the cotton iscondensed in a trumpet and passed in sliver form between the rollers Sand 6 over the knockoff motion 26 and then to a coiler shownschematically at 184 which coils the sliver into a receiving can. Thecoiler 184 is driven from shaft 27 by gears 185 and 186.

So long as the sliver retains the desired thickness the lever andhydraulic system remain stationary and the machine runs as described. ifa variation in sliver thickness occurs the roller 5 is either raised orlowered with respect to roller 6 so that the bellcrank lever 45 pivotsabout shaft 52. This pivotal movement is magnified by lever 67 and thelower end 107 of this lever causes the spool 111 to move axially in thehousing 110 so that fluid flows from inlet port 121 through one of theoutlet ports 122 or 123 to the appropriate side of the piston 135. Thepiston 135 thus moves and the piston rod shifts the belt 146 axially sovarying the transmission ratio between the cone 144 and 145. The speedof rotation of shaft 173 is thus changed, so changing the speed of shaft183 and changing the speed of the lap feed. The rate of feed of cottoninto the carding machine is thus changed, the change being in such asense as to vary the thickness of the sliver leaving the cardingmachine, so that this regains the desired thickness.

The low friction in the lever system and in the valve system make theapparatus very sensitive to even very small changes in sliver thickness,and the arrangement ensures that a correcting factor is continuouslyapplied to the lap feed whenever the sliver deviates from the requiredthickness. This continuous correction movement ceases immediately thesliver possesses the desired thickness and does not restart until thesliver again deviates from standard.

lclaim:

1. Apparatus for controlling the count of a sliver fed from a cardingmachine having a drive mechanism, said apparatus comprising a. aseparately driven feed drive;

b. sliver sensing means having two sensing elements between which saidsliver passes;

c. means mounting one of said elements for movement relative to theother of said elements in accordance with variations in sliver thicknessfrom a normal thickness;

d. lever means comprising 1. a housing;

2. a bellcrank lever pivotally mounted in said housing and having anupper arm rotatably supporting said one of said elements, and a lowerarm;

3. a magnifying lever having upper and lower ends, the

upper end of said magnifying lever being pivolnlly connected to thelower arm ofsaid hcllcrnnk lever;

4. a control lever having one end pivotally mounted within said housingand the other end pivotally connected to said magnifying lever adjacentthe upper end of said magnifying lever, said lever means being operableby movement of said one of said elements to produce a correspondingmagnified movement at the lower end of said magnifying lever;

e. valve means coupled to the lower end of said magnifying leverresponsive solely to said magnified movement and movable thereby from aninitial setting related to the normal thickness of the sliver;

f. a fluid-operated motor, flow of fluid to which is controlled by saidvalve means, the direction of flow being dependent on the sense ofmovement of said valve means from said initial setting and the rate offlow varying continuously with the distance of movement of said valvemeans from said initial setting; and

g. variator control means having an input shaft coupled to the drivemechanism of said carding machine and an output shaft coupled to saidseparately driven feed drive, said variator control means being furthercoupled to said fluid operated motor to vary its output speed andthereby cause correction of the sliver size at a rate and in a directiondependent on the rate and direction of flow of said fluid andindependently of the position of said variator control means.

2. Apparatus as claimed in claim 1 wherein a. the pivotal connectionbetween the lower arm of said bellcrank lever and the upper end of saidmagnifying lever comprises 1. a first pair of bearings the outer racesof which are secured to the lower arm of said bellcrank;

2. a second bearing, the outer race of which is secured to the upper endof said magnifying lever; and

3. a first shaft mounted in said housing, the inner races of said firstpair of bearings and second bearing being secured to said first shaft;and wherein b. the pivotal connection between said control lever andsaid magnifying lever comprises 1. a third bearing, the outer race ofwhich is secured to said magnifying lever;

2. a fourth pair of bearings, the outer races of which are secured tosaid control lever;

3. a second shaft mounted in said housing, the inner races of said thirdbearings and fourth pair of bearings being secured to said second shaft.

3. Apparatus as claimed in claim 2 further including means for rotatingsaid first and second shafts.

4. Apparatus as claimed in claim 3 in which said means for rotating saidfirst and second shafts comprises a one-way clutch transmission from oneof said levers to said first shaft to rotate said first shaft only in asingle predetermined direction on movement of said levers.

5. Apparatus as claimed in claim 1 wherein said sensing elementscomprise a pair of rollers.

6. Apparatus as claimed in claim 1 wherein said variator control meansfurther comprises a variable speed drive transmission between said inputand output shafts and controlled by said motor.

7. Apparatus as claimed in claim 6 wherein said transmission is avariable belt and cone transmission, and said motor operates to movesaid belt.

9 1 0 8. Apparatus as claimed in claim 1 wherein said pivotal aneccentric. mounting for said bellcrank lever comprises a first shaftjour- 10. Apparatus as claimed in claim 1 further comprising biasnaledeccentrically in said housing. ing means acting on said magnifying leverand said bellcrank 9 Apparatus as claimed in claim 1 wherein Said meanslever inadirection to press said sensing rollers together. pivotallymounting said control lever in said housing includes

1. Apparatus for controlling the count of a sliver fed from a cardingmachine having a drive mechanism, said apparatus comprising a. aseparately driven feed drive; b. sliver sensing means having two sensingelements between which said sliver passes; c. means mounting one of saidelements for movement relative to the other of said elements inaccordance with variations in sliver thickness from a normal thickness;d. lever means comprising
 1. a housing;
 2. a bellcrank lever pivotallymounted in said housing and having an upper arm rotatably supportingsaid one of said elements, and a lower arm;
 3. a magnifying lever havingupper and lower ends, the upper end of said magnifying lever beingpivotally connected to the lower arm of said bellcrank lever;
 4. acontrol lever having one end pivotally mounted within said housing andthe other end pivotally connected to said magnifying lever adjacent theupper end of said magnifying lever, said lever means being operable bymovement of said one of said elements to produce a correspondingmagnified movement at the lower end of said magnifying lever; e. valvemeans coupled to the lower end of said magnifying lever responsivesolely to said magnified movement and movable thereby from an initialsetting related to the normal thickness of the sliver; f. afluid-operated motor, flow of fluid to which is controlled by said valvemeans, the direction of flow being dependent on the sense of movement ofsaid valve means from said initial setting and the rate of flow varyingcontinuously with the distance of movement of said valve means from saidinitial setting; and g. variator control means having an input shaftcoupled to the drive mechanism of said carding machine and an outputshaft coupled to said separately driven feed drive, said variatorcontrol means being further coupled to said fluid operated motor to varyits output speed and thereby cause correction of the sliver size at arate and in a direction dependent on the rate and direction of flow ofsaid fluid and independently of the position of said variator controlmeans.
 2. a fourth pair of bearings, the outer races of which aresecured to said control lever;
 2. a bellcrank lever pivotally mounted insaid housing and having an upper arm rotatably supporting said one ofsaid elements, and a lower arm;
 2. Apparatus as claimed in claim 1wherein a. the pivotal connection between the lower arm of saidbellcrank lever and the upper end of said magnifying lever comprises 2.a second bearing, the outer race of which is secured to the upper end ofsaid magnifying lever; and
 3. a first shaft mounted in said housing, theinner races of said first pair of bearings and second bearing beingsecured to said first shaft; and wherein b. the pivotal connectionbetween said control lever and said magnifying lever comprises
 3. amagnifying lever having upper and lower ends, the upper end of saidmagnifying lever being pivotally connected to the lower arm of saidbellcrank lever;
 3. a second shaft mounted in said housing, the innerraces of said third bearings and fourth pair of bearings being securedto said second shaft.
 3. Apparatus as claimed in claim 2 furtherincluding means for rotating said first and second shafts.
 4. Apparatusas claimed in claim 3 in which said means for rotating said first andsecond shafts comprises a one-way clutch transmission from one of saidlevers to said first shaft to rotate said first shaft only in a singlepredetermined direction on movement of said levers.
 4. a control leverhaving one end pivotally mounted within said housing and the other endpivotally connected to said magnifying lever adjacent the upper end ofsaid magnifying lever, said lever means being operable by movement ofsaid one of said elements to produce a corresponding magnified movementat the lower end of said magnifying lever; e. valve means coupled to thelower end of said magnifying lever responsive solely to said magnifiedmovement and movable thereby from an initial setting related to thenormal thickness of the sliver; f. a fluid-operated motor, flow of fluidto which is controlled by said valve means, the direction of flow beingdependent on the sense of movement of said valve means from said initialsetting and the rate of flow varying continuously with the distance ofmovement of said valve means from said initial setting; and g. variatorcontrol means having an input shaft coupled to the drive mechanism ofsaid carding machine and an output shaft coupled to said separatelydriven feed drive, said variator control means being further coupled tosaid fluid operated motor to vary its output speed and thereby causecorrection of the sliver size at a rate and in a direction dependent onthe rate and direction of flow of said fluid and independently of theposition of said variator control means.
 5. Apparatus as claimed inclaim 1 wherein said sensing elements comprise a pair of rollers. 6.Apparatus as claimed in claim 1 wherein said variator control meansfurther comprises a variable speed drive transmission between said inputand output shafts and controlled by said motor.
 7. Apparatus as claimedin claim 6 wherein said transmission is a variable belt and conetransmission, and said motor operates to move said belt.
 8. Apparatus asclaimed in claim 1 wherein said pivotal mounting for said bellcranklever comprises a first shaft journaled eccentrically in said housing.9. Apparatus as claimed in claim 1 wherein said means pivotally mountingsaid control lever in said housing includes an eccentric.
 10. Apparatusas claimed in claim 1 further comprising biasing means acting on saidmagnifying lever and said bellcrank lever in a direction to press saidsensing rollers together.